US7121102B2 - Precooler/chiller/reheater heat exchanger system for providing warm dried air - Google Patents
Precooler/chiller/reheater heat exchanger system for providing warm dried air Download PDFInfo
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- US7121102B2 US7121102B2 US10/879,224 US87922404A US7121102B2 US 7121102 B2 US7121102 B2 US 7121102B2 US 87922404 A US87922404 A US 87922404A US 7121102 B2 US7121102 B2 US 7121102B2
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- Prior art keywords
- heat exchanger
- air
- refrigerant
- moisture
- chiller
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- 239000003507 refrigerant Substances 0.000 claims abstract description 48
- 239000007788 liquid Substances 0.000 claims description 11
- 238000003303 reheating Methods 0.000 claims description 8
- 238000005219 brazing Methods 0.000 claims description 7
- 238000001035 drying Methods 0.000 claims description 6
- 238000005496 tempering Methods 0.000 claims 5
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 abstract description 17
- 238000009826 distribution Methods 0.000 abstract description 3
- 239000003570 air Substances 0.000 description 101
- 238000000926 separation method Methods 0.000 description 11
- 238000009833 condensation Methods 0.000 description 7
- 230000005494 condensation Effects 0.000 description 7
- 239000012530 fluid Substances 0.000 description 6
- 230000005484 gravity Effects 0.000 description 6
- 238000005057 refrigeration Methods 0.000 description 5
- 238000001816 cooling Methods 0.000 description 3
- 230000006870 function Effects 0.000 description 3
- 239000007789 gas Substances 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 3
- 239000000203 mixture Substances 0.000 description 3
- 238000009825 accumulation Methods 0.000 description 2
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 2
- 229910052782 aluminium Inorganic materials 0.000 description 2
- 238000007791 dehumidification Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000037361 pathway Effects 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 238000007605 air drying Methods 0.000 description 1
- 239000012080 ambient air Substances 0.000 description 1
- 230000000712 assembly Effects 0.000 description 1
- 238000000429 assembly Methods 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000005266 casting Methods 0.000 description 1
- 238000004581 coalescence Methods 0.000 description 1
- 239000002826 coolant Substances 0.000 description 1
- 239000000112 cooling gas Substances 0.000 description 1
- 239000000110 cooling liquid Substances 0.000 description 1
- 230000001351 cycling effect Effects 0.000 description 1
- 230000006837 decompression Effects 0.000 description 1
- 238000009413 insulation Methods 0.000 description 1
- 230000001788 irregular Effects 0.000 description 1
- 239000007791 liquid phase Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000011159 matrix material Substances 0.000 description 1
- 239000012071 phase Substances 0.000 description 1
- 238000003752 polymerase chain reaction Methods 0.000 description 1
- 229920006395 saturated elastomer Polymers 0.000 description 1
- 238000004513 sizing Methods 0.000 description 1
- 230000035900 sweating Effects 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
- F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
- F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
- F24F3/153—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification with subsequent heating, i.e. with the air, given the required humidity in the central station, passing a heating element to achieve the required temperature
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
- B01D—SEPARATION
- B01D53/00—Separation of gases or vapours; Recovering vapours of volatile solvents from gases; Chemical or biological purification of waste gases, e.g. engine exhaust gases, smoke, fumes, flue gases, aerosols
- B01D53/26—Drying gases or vapours
- B01D53/265—Drying gases or vapours by refrigeration (condensation)
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D9/0093—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
Definitions
- the present invention relates to the art of heat transfer; more particularly, to heat exchangers for use in refrigerated air drying; and most particularly to a precooler/chiller/reheater (“PCR”) system having an improved layout for one-step brazing of combined plate assemblies, easy scalability, improved operating efficiency, and reduced manufacturing cost.
- PCR precooler/chiller/reheater
- Refrigerated air driers are well known in the art of air conditioning.
- warm, moist air such as from the interior of a factory, and which typically is compressed, is cooled and dried and then conveyed to a location where it is used.
- This is known in the prior art to be accomplished by using air- or water-cooled aftercoolers, moisture separators, and air dryers.
- Air dryers are available in many different types, and the present invention is illustrated with a non-cycling direct expansion refrigerated air dryer wherein the compressor operates continuously.
- This type of air dryer effectively reduces water content in compressed air by physically chilling the compressed air directly with a refrigeration circuit and thus reducing the capacity of the compressed air to hold water vapor.
- Water vapor in the chilled compressed air condenses as liquid droplets as the temperature of the compressed air is lowered to a desired dew point, typically about 40° F.
- the combination of chilled air and water droplets flows through a moisture separator that mechanically removes the droplets from the air stream.
- the main components in this type of refrigerated air dryer are a refrigeration system, a moisture separator, and two air heat exchangers.
- the first of these heat exchangers is a precooler/reheater. It precools warm saturated compressed air from an air compressor aftercooler by transferring heat to chilled air that is being returned from the moisture separator.
- This heat exchanger reduces some of the cooling load that the refrigeration system would otherwise have to handle in subsequent dehumidification of the air. The refrigeration system becomes smaller, requiring less power for thriftier operation.
- the precooler/reheater heat exchanger is also known in the art as the “economizer” because of this benefit.
- Another benefit offered by this first heat exchanger is that it reheats the chilled air coming from the moisture separator, as described below. As noted above, reheating the chilled air reduces the chances that low ambient conditions can cause condensation in the air line downstream of the dryer and also reduces the likelihood of pipeline condensation or “sweating” that can occur on chilled surfaces in humid use conditions downstream of the PCR system.
- the second heat exchanger is a refrigerant-to-air chiller that takes the precooled air from the first heat exchanger and chills it to the desired dewpoint temperature by transferring heat from the air into a cold refrigerant on the other side of the heat exchanger, thereby causing condensation of water from the air. After being thus chilled, the air enters a moisture separator to remove any remaining condensed water, and then the air is returned to the cold side of the first heat exchanger for reheating and exit from the PCR.
- a prior art PCR in accordance with these disclosures comprises a precooler/reheater heat exchanger, also known as a precooler and reheater core, and a chiller heat exchanger, also known as a chiller core, in adjacent relation.
- Warm compressed air is passed through the precooler/reheater heat exchanger, and then directly through the chiller heat exchanger serially in a first direction, and then through a moisture separation means wherein water condensed in the chiller heat exchanger is collected and drained.
- the dried, cooled air is collected and directed via a return manifold to pass through the reheater side of the precooler/reheater heat exchanger in a second direction substantially perpendicular to the first direction.
- the prior art PCR design requires that the precooler/reheater core sections and the chiller core sections be stacked and brazed in two separate operations. After brazing is completed, manifolds are welded to the individually brazed cores, and then the individual cores and moisture separator sections are welded together to complete the assembly. What is needed in the art is an arrangement wherein all three sections may be stacked and brazed efficiently in one sub-assembly.
- the prior art PCR requires a large and complex return manifold to direct the compressed air flow from the moisture separation section to the reheater section.
- This manifold is typically a large and complex aluminum casting, the size of which cannot be readily altered to accommodate larger or smaller capacity heat exchangers as may be desired for various end-use applications.
- What is further needed in the art is a simple, straight manifold, preferably formed of off-the-shelf stock, which may be easily shortened or lengthened to accommodate heat exchangers of greater or lesser capacity.
- the prior art PCR employs a five-piece refrigerant inlet manifold assembly to direct refrigerant flow into the chiller.
- An associated refrigerant system must include an expansion device such as a thermo-expansion valve or capillary tubes.
- an inlet manifold assembly wherein chilled liquid refrigerant is both flashed and distributed into the chiller heat exchanger without resort to other expansion devices.
- the prior art PCR employs cross-flow directions in both the precooler/reheater heat exchanger and the chiller heat exchanger. It is known that counter-flow heat exchangers can be more efficient and provide more uniform temperature profiles in the fluids within the heat exchangers. This is especially important in the refrigerant side of the chiller, as it is more likely to provide uniformly superheated refrigerant vapor exiting the chiller, thereby reducing the likelihood that any liquid refrigerant can leave the chiller and enter the refrigerant compressor downstream, and thereby improving the overall control of the air dryer operation. What is further needed in the art is a PCR wherein all heat exchange is performed in a counter-flow fashion.
- the prior art PCR has the precooler/reheater heat exchanger in mechanical contact with the chiller heat exchanger along their mutual length, allowing heat transfer therebetween which compromises the thermal efficiency of both and increases the thermal load on the refrigerant system.
- What is needed in the art is a means for insulating the precooler/reheater heat exchanger from the chiller to allow an air dryer manufacturer to reduce the capacity and cost of the appropriate refrigeration system for drying capacity of a given air dryer system.
- an improved precooler/chiller/reheater system in accordance with the invention comprises a first precooler/reheater heat exchanger and a chiller heat exchanger separated by a moisture removal section. All fluid flows are parallel to the physical contact between these units, such that fluid flows through the heat exchangers are counter-flow.
- a refrigerant source provides liquefied refrigerant to the chiller heat exchanger, wherein the refrigerant is flashed through a perforated distribution manifold along the plates of the heat exchanger to form an adiabatically-chilled liquid/gas mixture.
- the liquefied refrigerant is passed through a portion of the chilled air pathway to reduce the temperature of the refrigerant prior to its being flashed by the distribution manifold.
- FIG. 1 is a schematic diagram showing fluid flow in a prior art PCR system substantially as disclosed in U.S. Pat. No. 6,085,529;
- FIG. 2 is an isometric view of an embodiment of a prior art PCR system consistent with the schematic flow diagram shown in FIG. 1 ;
- FIG. 3 is an elevational cross-sectional view taken along plane 3 in FIG. 2 ;
- FIG. 4 is an isometric view from above of a first embodiment of an improved PCR system in accordance with the invention.
- FIG. 5 is an elevational cross-sectional view taken along plane 5 in FIG. 4 ;
- FIG. 6 is an isometric view of a flashing refrigerant distributor for use in a PCR system in accordance with the invention
- FIG. 7 is a longitudinal view of the distributor shown in FIG. 6 ;
- FIG. 8 is a front elevational view of a second embodiment of a PCR system in accordance with the invention, showing the core sections within;
- FIG. 9 is a side elevational view of the embodiment shown in FIG. 8 , showing use of rectangular manifolds.
- PCR system 10 includes a precooler/reheater core 12 and chiller core 14 abutting along interface 16 .
- System 10 is shown as it would appear in a refrigerated air dryer system for handling ambient air from either interior or exterior locations.
- Warm moist air 18 from the discharge of an air compressor aftercooler 20 enters core 12 of PCR system 10 through an inlet fitting 22 and a manifold 24 .
- Coolant or refrigerant from a source 26 including a compressor is supplied to chiller core 14 via a line 28 , inlet fitting 30 , and manifold 32 .
- Refrigerant is returned from core 14 via a manifold 34 , outlet fitting 36 , and line 38 .
- Chilled air 40 leaving chiller core 14 is conducted to precooler/reheater core 12 by manifold means generally designated 42 having a first section 42 - 1 contiguous with chiller core 14 and a second section 42 - 2 contiguous with both chiller core 14 and precooler/reheater core 12 .
- the sections 42 - 1 and 42 - 2 are disposed at substantially right angles to each other.
- First section 42 - 1 of manifold means 42 is in fluid communication with heat transfer passages (not shown) of chiller core 14 along substantially the entire vertical length of chiller core 14 as viewed in FIGS. 1 and 3 .
- Second section 42 - 2 of manifold means 42 has an outlet in fluid communication with heat transfer passages (not shown) of precooler/reheater core 12 and at the upper end of core 12 as viewed in FIGS. 1 and 3 .
- System 10 is oriented so that manifold section 42 - 1 is disposed generally vertically and manifold section 42 - 2 is disposed generally horizontally and is located above the cores 12 and 14 .
- a moisture separator in the form of a demister mesh pad 44 in manifold section 42 - 1 , preferably extending along the junction between the passages of core 14 and the interior of manifold section 42 - 1 .
- a condensate drain 46 at the lower end of manifold section 42 - 1 serves to remove separated moisture which drips from pad 44 by gravity.
- Demoisturized and reheated air 47 leaves precooler and reheater core 12 via a manifold 48 and an outlet 50 which is connected by a conduit (not shown) to a location of use of the processed air.
- the path of air traveling through PCR system 10 is indicated by the arrows in FIG. 1 .
- the portion 52 of the path is through the stacked arrangement of heat transfer passages in core 12 in heat exchange relationship with the alternating stack of heat transfer passages through which the chilled air 40 from core 14 passes.
- the portion 54 of the path is through the stacked arrangement of heat transfer passages in chiller core 14 which are in the alternating relationship with the series of stacked heat transfer passages which convey refrigerant in the direction of arrows 56 .
- the flows of precooled air 54 and refrigerant 56 in chiller core 14 are in a cross flow, i.e., substantially perpendicular, relationship. Chilled air leaving core 14 is conveyed to core 12 by manifold means 42 .
- Chilled air 40 flows along the stacked arrangement of heat transfer passages in core 12 which are in heat exchange relationship with the alternating stacked arrangement of heat transfer passages through which the warm, moist incoming air 18 / 52 flows.
- the flows of warm, incoming air and chilled air in core 12 are in a cross flow, i.e., substantially perpendicular, relationship.
- Chilled air 40 while in core 12 gains some heat from the warm moist air 18 / 52 entering PCR system 10 . This provides a precooling function to improve the overall efficiency and also simultaneously results in the dehumidified air being tempered by reheating for its ultimate use.
- Prior art PCR system 10 relies upon low exit face air velocity from the chiller core 14 to incorporate integral separation of condensate from air. Some droplet separation occurs in the heat transfer matrix of cores 12 and 14 .
- Wire demister mesh pad 44 mounted flush with the air side exit face of the chiller core 14 is intended to remove any remaining droplets suspended in the air flow; however, in practice droplets exiting the core and mesh near the top of the core may be carried over into the precooler/reheater core 12 , thus reducing the efficiency of the apparatus. It is both difficult and expensive to make manifold 42 large enough that tiny moisture droplets can settle by gravity rather than being carried over into reheater core 12 .
- an improved PCR system 10 ′ in accordance with the invention comprises a precooler/reheater core 12 ′ and a chiller core 14 ′ separated by a moisture separation section 100 .
- the cores 12 ′, 14 ′ are laid up like conventional heat exchangers of alternatingly connectable plates 112 , 114 , respectively, formed preferably of aluminum in known fashion, such that materials passing through the cores on opposite sides thereof travel in opposite directions, i.e., in counter-flow.
- the moisture separation section 100 is disposed between cores 12 ′, 14 ′, providing thermal separation thereby, and comprises a plurality of spaced-apart plates 102 providing a very large surface for coalescence and accumulation of water droplets at low air velocities.
- plates 102 , 112 , 114 , end frames 104 , and internal frames 106 are sized such that the entire assembly, as shown especially in FIG. 5 , may be laid up and then brazed in a single step in a conventional brazing oven (not shown).
- a moisture separator-to-reheater (second crossover) manifold 110 is also included between end frames 104 .
- Additional elements include an air inlet manifold 116 , precooler-to-chiller (first crossover) air manifold 108 (shown in FIG. 4 but not visible in FIG. 5 ), an air outlet manifold 118 , a sump 120 , a flashing refrigerant distributor 122 , and a refrigerant collector 124 .
- system 10 ′ obviously requires a conventional refrigerant source compressor, similar to source 26 shown in FIG. 1 but omitted from FIGS. 4 and 5 for clarity, for receiving spent refrigerant 123 from collector 124 and supplying compressed refrigerant 121 to distributor 122 .
- flashing refrigerant distributor 122 comprises a generally rectangular body 128 suitable for attachment to core 14 ′ as by welding.
- Distributor 122 is provided with means 130 , for example threads as shown in FIG. 6 , for attachment to a source ( 26 ) of pressurized, liquid refrigerant.
- a blind axial bore 132 extends within body 128 , and a plurality of transverse radial bores 134 in body 128 intersect bore 132 .
- An individual bore 134 is provided for each cooling passage in core 14 ′, and distributor 122 is oriented such that refrigerant flow from bores 134 is directed into core 14 ′.
- the diameter of bores 134 is selected to cause a predetermined pressure drop such that the pressurized, liquid refrigerant flashes from the liquid phase to the gas phase as it passes into the cooling passages of core 14 ′, thereby obviating the need for a capillary or thermal expansion valve for flashing as is known in the prior art.
- the diameters of various of radial bores 134 may be varied to compensate for pressure drop along axial bore 132 such that flows from radial bores 134 are equalized.
- the angle of intersection between radial bores 134 and axial bore 132 may also be varied to compensate for the pressure drop as well.
- Axial bore 132 may have side walls of a constant diameter, as shown in FIG. 7 , or the walls may be tapered or stepped to further control the pressure drop of the refrigerant across the length of distributor 122 .
- system 10 ′ is preferably oriented with manifold 110 at the top and sump 120 at the bottom, as shown in FIGS. 4 and 5 .
- This orientation optimizes separation of moisture droplets from the airflow at the lower end of chiller core 14 ′ and throughout moisture separation section 100 , and conveniently permits accumulation of separated moisture in sump 120 .
- a dam or knife edge 136 extends downward into sump 120 between core 14 ′ and section 100 to provide a preferred drip edge for condensation, preventing creep of condensate from core 14 ′ into section 100 .
- forming the PCR system 10 ′ as a stack of parallel plates and frames, while employing manifolds to guide the air being processed and the chiller refrigerant, provides several novel and significant benefits over prior art PCR systems:
- the system may be conveniently sized to meet any specific air flow and dehumidification requirement by the addition or subtraction of plates from either of the heat exchangers 12 ′, 14 ′ and/or the moisture separator 100 without requiring any change in end frames 104 or internal frames 106 . See, for example, the difference in size between embodiment 10 ′ ( FIG. 5 ) and embodiment 10 ′′ ( FIG. 8 ). Because manifolds 108 , 110 , 116 may be readily fabricated from linear stock, such as rectangular stock ( FIGS. 8 and 9 ) or hemi cylindrical stock ( FIGS. 4 and 5 ), longer or shorter manifolds are readily and inexpensively provided, in contrast to prior art PCR system 10 ( FIGS.
- PCR system 10 ′ may be laid up and braze-assembled in a single brazing step, whereas prior art PCR system 10 requires a plurality of separate brazing steps.
- warm, moist air 18 enters system 10 ′ and is distributed into precooler/reheater heat exchanger 12 ′ via manifold 116 .
- Air 18 flows upward through core 12 ′ and is turned via a mitered section (not visible) in core 12 ′ such that air flow is directed sideways from core 12 ′ through a core exit 101 into manifold 108 .
- the partially-cooled air is conveyed by manifold 108 to a side entrance 103 in chiller core 14 ′, is turned by another mitered section (not visible) to flow downwards through core 14 ′ to an exit 105 into sump 120 .
- Compressed, liquid refrigerant 121 is supplied from a source (not shown) into distributor 122 at the lower end of core 14 ′ whence the refrigerant flashes via bores 134 to a cooling gas/liquid mixture in known fashion.
- the flow rate and thermal load are adjusted preferably to provide a dew point of about 40° F. in the dried air 111 exiting core 14 ′.
- Cool gas/liquid mixture flows upwards in core 14 ′ in counterflow to air 111 .
- Air flowing downward in core 14 ′ is cooled by heat exchange through plates 114 .
- Condensed water 107 drains by gravity from core 14 ′ into sump 120 and may be removed therefrom via drain port 109 .
- Air 111 is then directed upwards through moisture-removal section 100 wherein any residual moisture droplets are coalesced and returned by gravity to sump 120 .
- Plates 102 may be provided with fins or other appendages (not shown) in known fashion to promote surface turbulence and increased surface/air contact within section 100 .
- Chilled, dried air 113 exits section 100 into manifold 110 wherein it is conveyed to the opposite side entrance 115 to core 12 ′.
- Air 113 passes downwards in core 12 ′ in counterflow to air 18 and is warmed by heat exchange therewith through the walls of plates 112 . Warmed air 47 is collected by manifold 118 and is discharged from system 10 ′ for use.
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Abstract
Description
Claims (18)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
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US10/879,224 US7121102B2 (en) | 2004-06-29 | 2004-06-29 | Precooler/chiller/reheater heat exchanger system for providing warm dried air |
Applications Claiming Priority (1)
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US10/879,224 US7121102B2 (en) | 2004-06-29 | 2004-06-29 | Precooler/chiller/reheater heat exchanger system for providing warm dried air |
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US20050284157A1 US20050284157A1 (en) | 2005-12-29 |
US7121102B2 true US7121102B2 (en) | 2006-10-17 |
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US20060010887A1 (en) * | 2004-07-13 | 2006-01-19 | Byeong-Seung Lee | Plate heat exchanger with condensed fluid separating functions and its manufacturing method |
WO2008082408A1 (en) * | 2006-12-29 | 2008-07-10 | Carrier Corporation | Economizer heat exchanger |
US20110100594A1 (en) * | 2009-05-06 | 2011-05-05 | Api Heat Transfer Inc. | Water separator and system |
US20120279252A1 (en) * | 2011-05-06 | 2012-11-08 | Carlin John A | Modular construction compressed air/gas dryer system with filtration |
US8783057B2 (en) | 2011-02-22 | 2014-07-22 | Colmac Coil Manufacturing, Inc. | Refrigerant distributor |
WO2014126598A1 (en) * | 2013-02-14 | 2014-08-21 | Api Heat Transfer Inc. | Precooler/chiller/reheater heat exchanger system |
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US20140261764A1 (en) * | 2013-03-15 | 2014-09-18 | Water-Gen Ltd. | Dehumidification apparatus |
US9021817B2 (en) | 2012-07-03 | 2015-05-05 | Parker-Hannifin Corporation | Monolithic construction compressed air/gas dryer system with filtration |
US20160023127A1 (en) * | 2014-07-25 | 2016-01-28 | Hanwha Techwin Co., Ltd. | Separator |
US9482453B2 (en) | 2010-01-15 | 2016-11-01 | Ingersoll-Rand Company | Air dryer assembly |
US20230152042A1 (en) * | 2020-04-06 | 2023-05-18 | Vahterus Oy | A plate heat exchanger arrangement |
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US7343755B2 (en) | 2006-01-04 | 2008-03-18 | Flatplate, Inc. | Gas-drying system |
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US20130153170A1 (en) * | 2009-05-06 | 2013-06-20 | Api Heat Transfer Inc. | Precooler/Chiller/Reheater Heat Exchanger System |
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